Centrifugal dust separator



May 18, 1948. w. HlLLS CENTRIFUGAL DUST SEPARATOR Filed Feb. 14, 1945 6 Sheets-Sheet l IINVENTOR. I les/Ae 14 /'//'//5 ATTORNEY May 18, 1948. w. HILLS CENTRIFUGAL DUST SEPARATOR Filed Feb 14, 1945 6 Sheets-Sheet 2 R5 v M EH M V 7 mW FIE y 8, 1948. L. w. HILLS v CENTRIFUGAL DUS'T SEPARATOR Fild Feb. 14, 1945 6 Sheets-Sheet 3 FIE-1 Ala-L.

. INVENTOR Zes/ie M4 hW/s QZZE? ATTORNEY May 18, 1948. HILLS 2,441,631

CENTRIFUGAL DUST SEPARATOR Filed Feb. 14, 1945 6 SheetsSheet 4 65 FIE E INVENTOR. Les/is 14 1717/5 y I I 42m ATTORNEY May 18, 1948. L. w. HILLS 2,441,631

CENTRIFUGAL D UST SEPARATOR Filed Feb. 14, 1945 s Sheets-Sheet 5 F" JLIE E 9.5a g% .95

INVENTOR. Les/is W H/'//5 May 18,1948. L, HILLS 2,441,631

- CENTR'IFUGAL DUS'T SEPARATOR Filed Feb. 14, 1945 a Sheets-Sheet e IN VEN TOR. Les/fa 14 1607/5 gQwk /u ATTORNE Y Patented May 18, 1948 Leslie W. Hills, San Francisco, Calif., assignor to Hills Bros. Coffee, Inc. San Francisco, Calil'., a corporation of California Application February 14, 1945, Serial No. 577,766

This invention relates generally to apparatus a for removal of dust from dust ladene'd air or other gases. In particular the invention relates to dust separating apparatus of the centrifugal or rotary type, in which centrifugal forces are utilized effecting the desired separation.

Most industrial equipment for the handling and separating of dust from air or other gases makes use of the conventional'cyclone separator. Generally the fan or blower used with the cyclone has more centrifugal effect, this causes a disproportionate increase in the energy loss.

It is an object of the present invention to provide centrifugal dust-separating equipment capable of imposing centrifugal separating forces of relatively high order on the dust particles, without however occasioning high energy losses in the system.

Another object of the invention is to provide apparatus of the above character which is capable of imposing relatively high centrifugal forces for a relatively longinterval of time, thus promoting high separating efliciency. 13 a A further object of the invention is to provide apparatus in which relatively high airvelocities are utilized, as for example movement of the order of-15,00'0 feet per minute or more, together with means for recovering a substantial amount of energy from the air fiow and after removal of dust particles, whereby the net energy input for the system is not excessive compared w the input required for handling'an equal emount of air by conventional means and delivering the same ata comparable pressure head.

'A further objectof the in'vention'is to provide apparatus which is capable'of acting both as a highlyefiicient dust separator and as an air movingfan. a

Additional objects, oftheinvention will appear from-the following description in which the preferred embodiments have been set forth in detail in conjunction with the accompanying drawing.

Referring to thedrawing; i i

Figure .1 is a side elevational view section,

'5 Claims. (01. 183-77) showing apparatus incorporating'the presentinvention.

. Figure 2 is an end'view of the apparatus shown in Fig. 1.

Figures 3 and 4 aredetails illustrating a desirable methodof curving the blades on the intake impeller. p

Figure 4a is'a' cross-sectional detail taken along the line4w4a of Figure 1.

-" Figure 4b is a cross-sectional detail taken along the line 4b-4b of. Figure 1.

Figure 4c is a cross-sectional detail taken along the line 40-40 of Figure 1. p 1

Figure 4d is a cross-sectional view taken along the line id-4d of Figure 1..

Figure 4e is a cross-sectionaldetail showing a modification of Figure 1 for adjusting the orifice Figure 5 is azside elevational view in' section, illustrating a modified embodiment of the invention difiering from Figure 1 particularly in the construction of the outlet or discharge turbo rotor. v

' Figure 6 is a diagrammatic detail illustrating a desirablecurvature ofthe vanes or blades for the discharge turbo rotor.

Figure 7 is a side elevational view in section, illustrating a further embodiment of the invention characterized by use of aligned intake and outlet openings.

to Figure '7, but modified in certain respects', p articularly in connection with the intake impeller.

Figure 9a shows asuitable throttling arrangement which can be utilized in conjunction'with conduit 89 of Flgure9.

Figure 10 isla diagrammatic sectional detail, illustratingsuitable contouring in arrangement of blades for theimpeller and turbo rotor of Figure 9. p

Figure 11 is a vector diagram serving to explain Figure 10. Y Figure 12 is a side elevational view showing a vertical type of mounting with a secondary cyclone, for the embodiment of Figure 1.

Figure 13 is a plan view of the arrangement shown in Figure 12. p

. Figure 14 is a side elevational view in section of a further embodiment, in which the separat- Figure 17 is a side elevational view illustratin another embodiment of the invention in'which the use of an external cyclone is omitted. V

Figure 18 is a cross-sectional viewtaken along the line |8-|B of Figure 17.

The present invention makes use of a dust separating chamber of restricted diameter and sub stantial length having inflow and outlet openings at its opposite ends. A driven impeller cated at the inlet is formed in such a manner as to-accelerate and deliver the dust lad'ened air .into the eparating chamber at relatively highzr'otary velocity; as for example velocityof thezorder. of 15,000 feet per minute or more. The separating chamber is -provided with :an annular :opening near :its' outlet for removing iseparated dust: to-

gether with part of the air flow. This .material can the passed through assrnall conventional cyclone separator having its "exhaust tc'onnected back to: the intake of thezmain separating-apparatus to form a closed circuit. -Attainment:of -veloci'ties of the' order: mentionedrequires considerable power, and in order to;avoid"excessiverpower zconsumption: discharge tmeanszis :providedat' the outlet end of the separating chamber for recovering-a1 substantiahamount:ofsenergyf from'rthe air flow. In the embodiments? to. :be-zhereaftendescribed this discharge means utilizes a turbo rotor..having -blades; acted .upon by; the air. :leaving the separating. chamber, i-wherebyia: considerable :amount' of kinetic energy is .recoveredzand the air finally delivered from the apparatus: at .ai..desired pressure head. The gas separating chamber-is proportioned so: that a, very appreciable time in- -terval :is'provided for. adequate and efiicient'separation of the dust particlesurider thercentriiugal forces to'which theyare. subjected.

:The embodiment. shown :in'Figure .1 consists era rotary impeller 2 I, together" with" a turbo: rotor 22. A gas separating chamber 2.3,w-l iicl'r irrthis embodiment: is :cylindrical. shaped, aextends betweenxthe impeller and the turbo: rotor; and is in :axialalignment'with..the same. .Inthis instance the separating chamber can have 1a length of .fromc3t toi4- times its diameter. The impeller and *rotor 'are' secured'torra common operating shaft .24 .carried by suitable bearings .2fianda2'l, and

adapted to be dri-ven "by suitable means: suchas an electric motor.

Conduit-28serves to supp y dust ladened air to the intake opening 30 of the dust separating chamber. -This intakeopening is circular incontour. .and. is formed in the.end wall"29. The point .of attachment of conduit 28 within .walll zlis shown reinforced by the circularly bent; tube 31.

The impeller 2| is constructed in such a manner as to impart a relativelyhighrotary velocity to air within the separating chamber'23. In'fthis instance the impeller consists of circumferentially spaced'blades or'vanes'32' attached to theside .plate 33 and the hub 36. The-hub'in turn iskeyed to the shaft 24. A suitable form for the blades 32 is shown in Figures 1, 3 and 4. Leading edge-"portions"32a, on the inlet side 'of the impeller, are curved forwardly as illustrated, andprfertrbly .4 conform to the surface of a cylinder. The tip portions 321) are curved forwardly, preferably to conform to the surface of a cylinder, in order to give a relatively high rotational velocity to the discharging air. Cylindrical curvature for both the entry and tip portions 320. and 32b provide a blade structure which is easy to manufacture while at the same time having desirable flow characteristics.

At or near the outlet 38 of the separating cham- 'ber 23 there is an annular orifice 39 for removal of separated dust particles.

The dust discharging through orifice 39, together with a portion of the air flow,-is received in an annular chamber 4|,

ure 4c) and -provided with a tangentially conpreferably for-medi-n the shape of a volute (Fignected dischargeuconduit 42. In the particular detail construction indicated orifice 39 is formed between the end edge of the separating chamber 23 and a circular reinforcing tube 43.

Theiturbo rotor 22 in this instance consists'of circumferentially spaced blades which are carried rbyzthe'endtplate-flfi and the retaining ring '41. End plate' lfi is-attached to the hub lil, which in. turnis-keyed tothe shaft 25. Blades Mare curved backwardlywithrespect to both entrance and exitedges (Figurex4b)',-'so thatrrotatingair discharging from theseparating-v chamber acts upon the vanesto im-particonsiderable rotational torque to the turbo rotor-'anditheshaft 2 par ticularlywhen handling relatively large' volumes ofair. In this mannerconsiderable energy is recoveredan'd at the same time the absolute velocity of the-air delivered from the blades of the turbo rotor is greatly reduced.

:Surroundingtheturbo rotor 22 there is a casing '5l 'which -islikewise preferably formed as a volute, and is: provided with. a-tangential discharge pipe 52. Theuse of a volute in" this manner serves to convert. the kinetic energy of the-air streams delivered by the turbo rotor, to the desired pressure head inthe-discharge conduit-52, without undue loss of energy.

-While"the=apparatus described above isoperable by itself, itis desirable in commercial installations to connectthe conduit 42'with some suitable secondary dust collector, such as a dust separator or collector of the cyclone type. Because such a cyclone may not efiiciently remove dust,

theexhaust' from the same is preferably connected back to the intake side of the system, as

will be presently explained in greater detail. To

facilitate return from the secondary cyclone I have showna return conduit 53 connected to an L 53wthrough the lower side of the conduit 28. A shroud or hood 54'wi-th a rounded nose (Figure 4d) isshown immediately below the "bearing 21 and about the L 5311. This construction permits the .passageof foreign materials such as strings, shavings and theelike, without possibility of obstructing theentrance to the impeller 21 because -of fouling ofssuehmaterial-lon the bearing suppendent upon the separating requirements, the

operating head and upon the construction of the impelle and turbo rotor, In general it is desirable that the speedl'be such that the rotational velocities created in the separating chamber 23, are of the order of say 15,000 feet'per minute or more. Within the separating chamber the air currents swirl in a rotary direction and also progress through the chamber toward the turbo rotor 22. In other words the locus of an imaginary point in this air flow issubstantially a helix. Within the separating chamber dust particles are subjected to relatively high centrifugal forces whereby they are impelled outwardly in close proximity with the inner peripheryof the chamber walls. Dust particles are largely concentrated in an outer layer or zone of the air flow. 'Near the outlet end of the separating chamber the zone of air just mentioned'is caused to discharge through the annular orifice 39 into the volute H. The amount of the air flow diverted in this manner may be from to ormore of the flow entering the impeller ilfdepending on the desired efiiciency of dust collecting, and may be adjusted by the provision of suitable'meansfor adjusting the width of orifice :39 (Figure 4e) and/or by throttling means in the conduit leading'to'the cyclone, as will be presently explained in connection with Figure 9a; This material immediately passes to the secondary cyclone or collector, where a large part of the dust is'removed and collected, and the remaining air with some dust particles then returned -by wayof con-' duit 53. The bulk of the "air which doesnot'pass through orifice 39 acts upon the bladeso'f'the turbo rotor 22, whereby the "rotary velocity" of the air currents is greatly reduced and'a very substantial amount'of mechanical energy is re-' turned to the system. Air discharged into the volute 5! produces a desirable and usable-pressure head in the final discharge conduit 52. j

It will be evident from the above that the equipment described makes possiblehighly' eflicient centrifugal separation of dust particles,without wasteful energy consumption. Efficiency-of centrifugal separation is made possible not only becauseof the high rotational velocities'which pro duce a high centrifugal effect, but because the dust particles during separation and removal are not caused to pass through zones-of excessive turbulence'or through air currents traveling-in directions differing from the desired direction of movement of the particles. In additlonthe pro portioning of the separating chamber insures a very substantial time interval during whichthe dust particles are subjected to centrifugal forces and before the separated particlesare removed through the annular orifice 39. Higherair ve locities, say 30,000 feet per minute,imayzmake necessary a careful streamlining 'of" the "rotor blades for higher eificiency, even to' thepoint of approaching the exacting curvatures of. an air foil section.

In the embodiment of Figure 5 the impeller 2 and the turbo rotor 56 'are mounted ,:upon the shaft 51, as explained for Figure 1.-'Shaft 51 is carried by the bearings 58 and 59, and the latter bearing is preferably carried by the radially extending vanes 6|. These vanes are; preferably formed to provide a cross-sectional contour more or less similar to an aerofoil', in order; to provide a minimum of air flow resistance. Likewise a streamlined shrouding 62 is provided for the bearing 59 and for the hub 36 of the impeller 2!.

Blades 63 for the turbo rotor 56 arespacedcircumferentially and are mounted on, the hub 64.

These blades can be shaped substantially as shown in Figure 6, in order to be acted upon effectively by the air currents leaving the separating chamber, to thereby eificiently recover energy for the system; It will be noted that the impeller in this instance is constructed for straight through axial flow of air. Air delivered from the blades of the turbo rotor-is received in the shell or volute casing 61, and finally delivered to the tangentially connected discharge conduit 68.

The embodiment of Figure 5 operates in substantially the same manner as Figure 1. Energy is recovered from the air flow while the air is moving axially of the shaft 51, and without the necessity of first moving outwardly as in Figure 1. It will benoted that Figure 5 is not provided with a" conduit comparable to the conduit 53 of Figure 1. Therefore ifit is desired to effect a return from the secondary separator, this return should be at some suitable point to the inlet side of the apparatus, as for example to the conduit 28.

Figure? illustrates another form of the invention which avoids the necessity for the discharge shell or volute 5! of Figure 1, or 6'! of Figure 5. In this instance the gas separating chamber H is made similar to the separating chamber previously described, except that it is shown somewhat .shorterin length. A curved or elbowshaped conduit section 12 having a division plate 10 is shown connected to theinlet opening of the separating chamber. Both the impeller 2| and the turbo rotor 13- are mounted upon, the'common shaft 14, which in turn is carried by the bearings 16 and Ti. Turbo rotor 13 together with bearing ISis within a conduit '18, which is aligned with impeller 2| and the gas separating chamber H and which is in effect a portion of a discharge conduit. Conduit 18 should preferably be extended to a length of about 3 to 4 times its diameter in order to obtain maximum conversion of velocity head to pressure head. The turbo rotor 13 consists of circumferentially spaced blades 19 Which are carried by the inner hub 8i. Bearing 16 is supported by a plurality of radially extending and circumferentially spaced vanes 83, which engage air currents leaving the blades 19. shrouds 84 and are provided for the hub 8|, and the bearing 16, and these parts are streamlined to present-a minimum of air flow resistance. A suitable shaping for the rotor blades 19 and the stationary vanes 83 is shown in Figure 8. Blades 19 are shaped to be engaged by the rotating air currents leaving the separating chamber 1|; whereby the rotary velocity is reduced'to substantially zero and absolute velocities of these air currents are greatly reduced to thereby recover energy for the system. Air leaving the blades I9 retains some rotary velocity under optimum or normal flow conditions, but upon engaging the vanes- 83, the j direction of movement is changed whereby the air leaving these vanes flows axially of the conduit 78; Thus a, desired static pressure head is efficiently maintained Within the conduit 18, sufficient for example to convey the air flow to other parts of a pneumatlc system with which my apparatus is employed. The spacing between blades 83 should be about one-half to one-fourth their length as measured in the direction of the axis of rotation.

The remainder of the apparatus shown in Figure '7 is similar to the embodiments previously described. I Dust'centrifugally separated out in chamber II is removed through the annular ori fice 81 and is received in the volute 88. From thisvolute dust is removed through conduit 89, which may lead to a secondary, cyclone as previously described. 7 V

'7 9 The embodiment of Figure'Qissomewhat similar tolFi'gure 7, except that an'axi-al flow typeof impeller has been employed. Also in this in-. stance the secondary cyclone is illustrated, together :with a connection for reintroducing the exhaust of the secondary cycloneback into the intake'of the'impeller. Thus in this instance the impeller 9| and the turbo rotor 92 are mounted upon-the common shaft 93. The shaft 93 is axially aligned with the cylindrical gas separatingchamberBd. Inflow conduit 96 connects with the inlet endof the gasseparating chamber 94, through the flared or expanding section 91, and the shellifiB surrounding the turbo rotor 92 connects with the conduit section 99, and from thence to the discharge conduit I90. Annular orifice 3T, volute 83, and discharge conduit 89 are the same as Figure 7. A secondary-cyclone separator 80 has its'inletconnected to conduit 89, and its exhaust connected to a conduit 95 which'communicates withthe lower side of conduit '96. Within the conduit 96 there is a shroudingto form a passage 91a leading from conduit 95, and serving to deliver the returned air to the intake of the impeller IN. The differential pressure across'the cyclone is relatively high with resulting highflow velocities through the same, thus contributing to its efiiciency of separation. In fact the pressure difierential across the cyclone is in excess of the'overall pressure differential across the unit because of the high velocity of air discharged through dust conduit 89.

Figure 9a illustrates throttling means which canbe utilized in conjunction with conduit 89 for thepurpose of controlling the amount of air diverted from the main separating chamber to the cyclone 80. Briefly this throttling means consists of a movable deflecting plate or baflle 89a which can be adjustedby suitable means such as the screw'80b. Thus the discharge end of the conduit 89 can'be varied with respect to the cross-sectional flow area afiorded, in order to correspondingly vary the amount of dust ladened air passing through the conduit 89. It will be noted that this method of control increases the efficiency of separation of the cyclone 90 because all of the fiow is delivered tangentially near theperiphery of the cyclone chamber, and because the velocity head developed by throttling is effectively used in the cyclone. A means to control the operational pressure inthe cyclone is afforded in theoutlet control gate 95a. By adjusting this gate one may obtain a substantially atmospheric pressure at the dust outlet 80a at the bottom of the cyclone cone and permit the precipitated dust to fall into an open container.

The impeller 9| in this instance utilizes the curved circumferentially spaced blades IOI. As diagrammatically indicated in Figure these blades are formed to provide a forwardly curved discharge lip, thereby making possible a relatively high rotative velocity for air leaving the blades.

The shaft 93 is shownwith its one'end carried by the bearing I02 and its other end coupled to the electric motor I03. Motor I03 is provided with a streamlined shrouding I 04 and is supported by the radially extending stationary vanes I05. The number of vanes I05 is preferably incommensurate with the number of blades I03 on the rotor 92. Suitable shaping of the vanes I95, and'also the blades I06 of the turbo rotor 82, is illustrated in Figure 10. Here again the shaping of the blades for the turbo rotors is such as to recover energy from the-rotatingair leaving the gas separating chamber, while the stationary vanes I05 serve to deflect the air flow leavin the blades of the turbo rotor and to direct the same longitudinally of the conduit section 99. This arrangement together with the tapered construction of conduit section 99 insures effective building up of a desired pressure head in'conduit I00.

Figure 10 together with the vector diagrams of Figure 11 serves to illustrate movement of 'air through the apparatus of Figure 9 for two assumed inflow rates, one being a given maximum value andthe second being an assumed lower value. .In both Figures 10 and 11 it is assumed that the movement of the'blades l0! and I06 is upwardly, or in other words as Figure 9 is viewed from the right the rotation is clockwise. Vector VI at the right hand end of Figure 11 represents the direction and absolute velocity of air at the intake of the first rotor 9i at an assumed maximum value. Vector V2 represents the direction and velocity of the air flow relative to the blades WI, and as the air flow is leaving these blades. Vector V3 represents the blade velocity. Vector V4 represents the direction and absolute velocity of air flow leaving the blades. Vector V4 is likewise the direction and absolute velocity of air flow leaving the blades, but in this instance the velocity'is for an assumed inflow rate somewhat less than that'represente'd by vector VI. Vectors V5 and W5 likewise represent absolute velocity and direction of air flow within the separating chamber 9:1, for both the maximum and assumed lower rates. Vector V3 as it appears near the left hand end of Figure 11 again represents the velocity of blades I90. Vector V5 represents the velocity and direction of flow leaving blades 505, relative to the blades. Vector V 5 represents the absolute velocity and direction of air flow leaving the blades I06. Vector VG represents the velocity and direction of air flow leaving the blades for the assumed lower capacity. It will be noted that both vectors V6 and V6 are at minor angles'with respect to the stationary vanes tilt. Therefore for the assumed maximum and reduced inflow rates vanes l05 will'act upon the airflow with a -minimum amount of :change in direction offlow,

to cause effective conversion of velocity to pressure head within conduits'99 and I09. Likewise with the'flow rates and direction of flow represented by the vector diagram of Figure 11, vanes I05 can be substantially straight and substantially parallel tothe axis of shaft 93 except for streamlining of the same to reduce flow resistance and turbulence.

In actual practice the pressure head to which the device discharges (i. e. pressure head in conduit I00 of Figure 9) may vary from time to time or in diflerent installations. In general with an increase in such pressure head the flow rates are reduced and this results in an increase inthe number of turns the path of the air takes in passingthrough the separating chamber to the annular dust discharge orifice.

With the embodiments described above, the turbo rotor for normal capacities or flow rates between given maximum and minimum values will at all times be acted upon by the i such a fashion as to recover energy. However it should be noted that with an arrangement such as sown in Figure 9, at high delivery heads and with ab-- normally low flow rates the turbo rotor 92 will.

not recover energy but will in eiiect assist rotor 9| in building up the desired discharge head.

This 7 holds true with greater, eifect for the annular discharge turbo rotor 46 of Figure 1.: 1

Figure 12 illustrates" apparatus like Figure 1 mounted in a vertical position in conjunction with a secondary cyclone separator. Thusin this instance a suitable frame IIl'I serves to support the apparatus of Figure 1, and an electric motor I08 is directly connected to the operating shaft'24;

Conduit is connected to the intake side of the cyclone separator- I09; the exhaust of which connects with a cnduit'53. Figure 13' illustrates the arrangement of Figure 12 in plan. It will "be understood that the arrangement of Figures 12 and 13 can likewise'incorporate the throttlingiarrangement previously described with-reference to FigureSd. V

Figure 14 illustratesanother embodiment o'f the invention having certain parts similar to Figure 1', but utilizing a rotating rather than a stationary separating chamben; Thusin this instance impeller II I,mounted upon shaft 24, has'blades formed similar-to the impeller 2| 'of Figure 1, and directly mounted upon this impeller there is a cylindrically shaped dust separating chamber II2. To provide su'flicie'nt strength to withstand centrifugal forces; this chamber can be formed of separate inner and outer cylindrical walls I I2a and I I2!) which are attached together by webs or ribs I I20. The chamber is completely enclosed by the stationary housing I I3, which has an end wall -I I;;connectingwiththe inlet conduit 28; Collar ZBa -has' a minimum amount of clearance -withrespect to the impeller in-order to reduce leakage back to the intakerThe other end of housing -I I3 connects with the volute I I4,, corresponding to volute 4| of Figure 1, and terminates short of the adjacent end of the rotaryseparating chamber 112. "The free" end of rotating chamber II2','that is the end remote from'the'impeller I I I is spaced from the adjacent circular portion I I5 to form 'and resulting turbulence between the inner surface of chamber II2 anddthe rotating air currents. Air can be delivered from the blades of the impeller III at a speed no higher than that necessary to convey precipitated dust along the inner surface II2 thereby minimizing the turbulence of the air next to the surface 'I I2. Therefore the chamber rotates concurrently with the gases being subjected to centrifugal force, thereby minimizing any tendency to form a zone of turbulence adjacent the inner wall of the separating chamber.

It will be appreciated that the rotor type of gas separating chamber. as shown in Figure 14,

br I28. The impeller I29 can be made of vanes shaped-as shown in Figure 15a. Instead of using the conventional hub as in Figure 9, these blades are secured to a driim I3I which in turn is mounted upon the shaft I32. Drum I3I also serves to carry the vanes-for the turbo rotor I33 which can be shapedsimilar to the blades for the impeller '2I of Figures 5 and? but with the curvatures arranged to recover energy The intake end of drum-I3 I iss'trea'mlin'ed by the stationary conical shaped member I34, which is retained in place by suitable means such as the web I36, Conduit I3! is provided for the return of dustladened air from the external cyclone. Dust separated in chamber 128; passes through the annular orfice I38 which'dischar'ges into the volute I39 as previously describ'ed.- The turbo rotor I33 likewise dischargesinto the volute I4Ifwhicl1 connects tangntiallywith a discharge conduit. Shaft I32 is rdtated byjsuitable means such as a directly connectedelectric-motor. 9 r

"* 'Figur 16'- illustrates anembodiment somewhat similar to]-'Figure 15 but modified with respect toft'he shapingof a th gas chamber I 28 {In this instance the' inl et conduit I 42 connects withjthe "inletend of the gas separatingchamber I43, which'has a slight- 'tap'e'r; "The impeller I44 -is mounteizi upon {a 'I4 Ii which in turn is meun'ted' updn' theshaft I415 "Dr-um I46 in this instance-is somewhat -lo'ngerthan in Figur 15. A member I48 corresponds with member I34 of Figure 15 and inthis 'in'stanc itforms' a bearing forthe lnJet ehd-of shaft I4 'I.- A return conduit I49 is" also provided corresponding to-th-e conduit i I 31: .of. Figure .15. Turbo rotor I 5I can be substantially'thesame. as rotdr: I 33 of Figure 15. i The enlargedi end: of -gas: separating chamber, I43 is arran ed to dischar e separated dust through the annular orifice ,-I 52; in a similar manner tooriflc 8 9 l efl f. i Figures 17 and 18 show an embodiment in which an external cyclone. is omitted. The main part of the device in this instance is made as in Figure 15 but in place of volute I39 there is an annular chamber I56 having a side connection with a conduit I5I leading to the dust collecting receiver I58. A deflector I 59 serves to split and direct the flow as indicated whereby dust is deposited into receiver I 58. Therefore in this modification there is no bypassing of air back to the inlet.

It will be appreciated that various types of materials can be utilized in constructing the foregoing embodiments of the invention. Where the dust particles being carried by the air flow are abrasive in character, the walls of the separating chamber can be lined with suitable resilient material such as natural or synthetic rubber. Likewise various coating materials can be applied to the surfaces of the various parts exposed to the air flow, as for example coatings of thermo-plastic resins or like synthetic materials.

I claim:

1. In centrifugal dust separating apparatus, a separating chamber having spaced inlet and outopenings at its opposite ends, a driven impeller disposed near the inlet end of the chamber and having its axis coincide with the axis of the chamber, said chamber being mounted to rotate in unison with the impeller, said impeller being constructed to deliver dust 'ladened air to the separating chamber with relatively high rotary velocity about the axis of the chamber, said rotary velocity being in excess of the peripheral velocity of the impeller, and means located at the outlet of said dust outlet from said first rotor and V 3. In centrifugal dust separating apparatus, a 1

separating chamber having spaced inlet and outlet "openings at its opposite ends a iriven impeller located near the inlet and servingto deliver dust ladened air into the se arating chamber with relatively high rotary velocity about-theaxis of the chamber, the impeller having blades extending rorwardly in the directionpfairfi -therethrough so thatsaid rotary yelocity is in excess Qf the e i r el i qfnt e. mpell me n located at the periphery of the chamber near the outlet endot the same for removing centriiugally separateddust together with a portion of theair flow, said meansbeing spaced in an axialdirec- 1 from h im l e a d discha e mean ncluding a turborrotor acted pponby air current ch n omy a d ch mb and s rv n o effectively recover energyfiomthe same. 7

a 4. In centrifugaldust separating-apparatus,an impeller adapted to be driven and adapted to impart relatively high rotary velocity ;to air acted upon by the same, theimpellerhavingblades extending forwardlyinthedirection of air flo'w there'- through so that said rotary ivelocityfis inae'iccess ofthe rotary velocity "of the impellen 'a turbo rotor substantially aligned with tl' e akis of the first impeller butspaceddate'rally fromthe same, said rotor, having blades formed whereby rotary air currentsv acting upon the same serve to impart rotary torqu'eto thero'tonand *acdust separating chamber interposedbetween the, impeller and the rotor.

5. centrifugal dust separating, apparatus,- an impeller adaptedto be driven; andadaptedgtoj impart -relat-ively highrotaryvelocity to air acted upon the same," $17116 impe1ler having blades 38X- tending .forwardly in ;the;,directio n or-a-ir flow therethrough so that said rotary velocity isin excess of the peripheral velocityoftheimpeller, a turbo rotor substantially aligned with-the axis of the first L impeller but 3 1 340861 laterally; from the same, said rotor having backwardly curved'blades whereby rotar-y aircurrents acting upon the same servetoimpiart rotarytorque to therotor, adust separating I chamber interposed between the impeller and the rotor, and anaannular-orifice or opening at the discharge-end of the chamber and spaced axially from the -impeller. u

7 LESLIE 'WNHILLS.

REFERENCES CITED The following referen'cesiare of'record in the file of ';t'his pat1ent:

UNITED s'rrrrns PATENTS :FO'REiGN --PATENTS Number v Cou try v Date 570,355 Germany Feb. 21, 1933 573,905 ermany Ap'r."7, 1933 Certificate of Correction Patent No. 2,441,631. May 18, 1948.

LESLIE W. HILLS It is hereby certified that error appears in the printed specification of the above numbered patent requiring correction as follows: Column 10, line 65, for the Word and hyphen outread outlet; and that the said Letters Patent should be read With this correction therem that the same may conform to the record of the case in the Patent Office.

THOMAS F. MURPHY,

Assistant Commissioner of Patents. 

